US3160486A - Fluid operated timing apparatus - Google Patents

Description

Dec. s, 1964 Filed April 24, 1962 AIR COMP.

A. L. BuscH, JR

FLUID O'ERATED TIMI-NG APPARATUS 4 Sheets-Sheet 1 lill I 6o /es es 4- illli; l.

se 84 l s? 4o 75 78 67 se 20 if x xg' w SalI/27 y Adolphus L. Busch, Inventor A. L. BUSCH, JR

Dec. s, 1964 FLUID OPERATED TIMING APPARATUS 4 Sheets-Sheet 2 Filed April 24, 1962 n m Do n- Adolphus L. Busch, Inventor A. L. BuscH, JR 3,160,486

FLUID oPERATEn TIMING APPARATUS 4 Sheets-Sheet 3 Filed April 24, 1962 Adolphus L, Buch, Inventor Dec. s, 1964 BUSCH' JR 3,160,486

FLUID OPERATED TIMING APPARATUS Filed April 24, 1962 4 Sheets-Sheet 4 Adolphus TIL. yBusch, Inventor United States Patent O SJtSASo FLUHD QPERA'L'ED TlMlNG AARATUS Adolplius L. Busch, r., Hampton, Bethlehem Township,

Hunterdon County, PLE., assigner, by nresne assignments, to Gilbert d: Barker Manufacturing Company, a

corporation of Massachusetts Filed Apr. 24, 1962-, Ser. No. 189,92l 22 Claims. (Cl. 55-l62) The present invention relates to a nid operated timing apparatus. Particularly, the present invention relates to an apparatus adapted to provide mechanical and uid action in a predetermined timed manner, which apparatus operates solely by the employment of a fluid medium. More particularly, the present invention relates to a pneumatically operated timing apparatus, which apparatus permits predetermined timed mechanical action or pneumatic flow directing action in an alternating and cyclic manner. Further, the apparatus of the present invention is of a nature allowing the rapid preselection, control and adjustment of the total cyclic period of operating or actuating time or of those internal or individual cyclic periods of actuating time making up the total cyclic period of actuating time or of both total and internal periods of time. present invention relates to an air-operated timing apparatus, which apparatus effects external mechanical action or pneumatic action of a fluid flow directing means over a preselected total cyclic period of time as well asinternal periods of time. Even more particularly, the timing apparatus of the present invention permits the cyclic operation, that is, the alternating opening and closing by external mechanical action, of uid ilow directing valves over a predetermined and preselected period of time. Further, the present invention relates to a timing apparatus capable of permitting the cyclic and-alternating internal operation of a gaseous ilow directing reciprocating piston means in a preselected timed manner. Even still more particularly, the present invention relates to a gas operated timing apparatus which permits either by external mechanical action on valve means or internal pneumatic action on gaseous iiow directing means the predetermined alternating and cyclic introduction into and discharge of a gaseous stream from an apparatus for fractionating gaseous mixtures. Even more explicitly, the present invention relates to an air-operated timing apparatus adapted to open and close gaseous flow directing valve means in an alternating cyclic timed manner, thereby permitting the cyclic and alternating introduction of a gaseous feed stream at a relatively high pressure into one or more beds of adsorbent material, and the cyclic and alternating discharge of a secondary effluent gaseous stream from the adsorbent beds to a region of relatively low pressure. In an even narrower sense the present invention relates to a heatless fractionating apparatus for gaseous mixtures in combination with a Still omer particularly, the4 gas-operated timing apparatus, which total apparatus operates solely by the relatively high pressure gaseous stream supplied to it for fractionating purposes.Y

Cyclic timed action of either an external mechanical or internal fluid flow directing character over predetermined periods of time is frequently required in the operation of various apparatuses. This is particularly true where fluids including both liquids and gases are required to be introduced into or withdrawn from vessels, accumulators, pipelines, storage tanks and other open or closed fluid containers in a cyclic and alternating manner by the operation of valves or other fluid iiow directing or switching means.v The rapid cyclic and alternating operation of fluid ow directing valve means in a predetermined timed manner is of particular importance in the rapid alternating introduction or discharge of a 3,160,486 Patented Dec. 8, v1964 ICC iiuid stream into or from elongated vessels containing liquid, gaseous, solid or semisolid catalytic, absorbent, or adsorbent-material. Of special importance in the fractionating of a gaseous mixture in vessels containing solid subdivided -adsorbent material by the heatless fractionation method is the timed alternating and cyclic introduction into and discharge from the adsorbent vessels of a relatively high pressure feed stream of the mxture in question.

In the course of operation of the conventional apparatus required for heatless fractionation as shown by and described in U.S. Patent No. 2,944,627 to C. W. Skarstrom, issued July 12, 1960, the timed rapid and alternating introduction of the gaseous feed stream and the discharge of the gross secondary effluent is usually accomplished byelectrically powered, solenoid-operated flow switching valves. Generally, the opening and closing of the valve means is accomplished in timed response to the electrical current flowing in a solenoid coil or coils. Thus, the sequential operation of the iiow directing or flow switching valves is commonly effected by a mechanical or electrical timer, which may have either a preset, fixed timing cycle or a variable cycle time. These timing means commonly operate through an electricaly powered motor, which through a camshaft or other mechanism opera-tes electrical switches or -mechanically acting arms in a preselected timing sequence, which switches are connected to and electrically operate the solenoid means or coils, or which mechanically acting arms are directly connected to actuating means of the valve means, thereby effecting cyclic operation Vin the opening and closing of the valve means.

f Although the employment of electrically powered and operated solenoid means has been proven generally satisfactory in the Skarstrom method and apparatus and in other apparatuses requiring timed cyclic and alternating action, the use of `electrically powered means has limited potential. For example, the employment of electrically operated timing means is often precluded in atmospheres containing combustible vapors or dust wherein a danger of explosion exists. At the very least, the use of electrical timing means in these ,atmospheres requires special precautions and often complex safety shielding equipment to suppress electrical contact sparks and the other inherent explosive hazards of electricalV timing mechanisms. Additionally, electrical timing means requires the presence of or connection with an available electrical power source. In certain locationsl electrical power sources or connective means are not readily or economically available, while pneumatic or huid-operated sources of power are available. For example, diesel fuel, steam, or gasoline powered air compressors or liquid pumps which provide relatively high pressure fluids are commonly operated or frequently available even in remote areas having no direct access to sources of electrical power. The present discovery, therefore, permits the operation of a timing apparatus by vHuid pressure sources such as steam, oil, or gas-'powered pumps ortcompressors and the like withoutthe need for electrical power.

It is, therefore, an object of this invention to provide a fluid operated, nonelectrical cyclic timing apparatus. Another object is to provide a timing apparatusy for operation in atmospheres and areas of explosive tendencies which preclude the use of electrically powered timers or require special precautions for such timers. object is to provide a pneumatically operated timing apparatus permitting predetermined cyclic alternating timed mechanical action or internal fluid rtlow directing action lin remote areas where electrical power is not readily available. A further Objectis to provide an air operated timing apparatus permitting the predetermined timed mechanical operation of valves or pneumatic ow direct- Another ing means to control the cyclic and alternating ow of luid streams. An additional object is to provide a pneumatically operated cyclic timing apparatus capable of rapid adjustment and control of both the total cyclic time period and the internal or individual cyclic time periods of the total period. Another object is to provide a gaseous fractionating apparatus wherein the sole source of operative power is derived from the relatively'high pressure gaseous stream to be fractionated or a gaseous component thereof. The present invention and its objects will be more fully understood and clearly perceived from the following de- ,Y scription and claims read in conjunction with and with Y' reference to the accompanying drawings. in which:

FIGURE 1 is a sectional and schematic view of an external mechanical Yrod action timing apparatus in cornbination with an external uid power operating source, With the internal movable components of the timing apparatus in their positions at the start ofthe timing cycle,

and showing the external operatingrrod in its retracted.

position;

FIGURE 2 is a sectional and schematic view of an ext ternal mechanical rod action timing apparatus in combination with an external iiuid power operating source, with the internal movable components of the timing apparatus in their positions at the end of the first internal l tion with an-external gaseous power operating and feed'V stream source, with the internal movable components of the timing apparatus in their positions at the start of the timing cycle, and showing the introduction of a gaseous mixture feed stream into a first adsorbent vessel and the venting of a second adsorbent vessel; and

FIGURE 5 is a sectional and schematic View of an internal fluid ow directing timing apparatus in combination with an external gaseous power operating and feedv stream source, with the internal movable components of :the timing apparatus in their positions at the end of thesiirst internal cycle period of time, andY showing the introduction of a gaseous mixturerfeed stream into a secondad-lv sorbent vessel and the venting of a first adsorbent vessel. Mechanical Action Timing ./etpgrmrztus Referring now tothe drawings in detail and, in particular, to FIGURES l and 2 thereof, there is shown the preferred mechanical action timing apparatus 1t! of this invention, which timing apparatus comprises in combination an actuator body 2t) and a timing body il in a straight line abutting relationship. Detachably vmounted in an internally threaded recess is a domed accumulator vessel 60 of predetermined volume, which vessel is closed at its upper end and provided with threads 66 at its lower end for attachment in a fluid-tight manner through an -0-ring sealing gasket 67 to the .internal recess. Slidably mounted for reciprocating, huid-tight motionv within a central longitudinal cavity 21 of the ractuator body is a cylindrically shaped actuator piston 22 having a forward face 23 and a rear face 24. An actuator piston rod 25 is xedly mounted in threaded engagement with the actuator piston, and projects outwardly and externally from the center forward end of the actuator piston.

Actuator piston rod 25 'projects in a fluid-tight v'manner through the center of a stroke adjusting end piece 26, and has its forward end terminating externally with other mechanically operated mechanisms such as Ylarger diameter than that of actuator body cavity 2l and an annular internal shoulder V28 at the forward end'of the actuator body cavity. The stroke adjusting end piece is'mounted in a movable, fluid-tight manner through an O-ring sealing gasket 30 cradled in an annular ring-like projection 3l, which gasket maintains rm, fluid-tight contact at all times and positions with the internal surface of the actuator body cavity. VvThe actuator Ibody cavityV is maintained in a fluid-tight manner, despite the reciprocating movement of the actuator piston and the external portion of its piston rod, by allowing the actuator piston rod which moves with the actuator piston to be sealed and rmly and centrally supported by `O-ring sealing gaskets 32 and 33 as the rod projects through the center of the stroke adjusting end piece. The end piece 26 permits the effective length of actuator body cavity 21 and with it the amount of vtravel of actuator piston 22 and theexternal mechanical travel ofV actuator piston rod 25 to be readily controlled within limits by adjustment of the longitudinal position of thethreaded end piece within the. actuator body .cavity through an external knurled adjustment knob Y 34, which knob is integrally mounted with end piece 26.

v compartment comprises that space located to the rear of the rear lface of the actuator piston and peripheral ring projection 35, and thus lhas for an effective cross section area thetotal area defined bythe diameter of actuator body cavity 21. The second andi third actuator compartf 'that defined-,by the diameter of actuator piston rod 25.

'Considering now, in particular, timing body 40 and associated apparatus, there is shown a cylindrically shaped timing pistonSt) having a forward face 51 and a rear face 52, and slidably kmounted within a central longitudinal timing body cavity 53 for reciprocating, fluid-tight movement. Timing piston tends tobe retained in a forward,

predetermined position by the force of a coiled spring 54 held in compression within the timing body cavity,

this spring having one end mounted against the rear face ofV a rearmost annularfperipheral ring Vprojection on the V'timing piston. The otherend of spring 54 is mounted against la pressure range adjustment end piece 55y secured rin threaded engagement with the timing body in an internal recess of slightly larger diameter than timing'body of the actuator body. The projecting actuator rod by Y cavity l53, and having an annular internal shoulder 57.

Y End piece 55 is maintained in a fiuid-tight mannerwith the internal surface of the timing body cavity by an annular peripheral ring projectiony which by means of an annular recess supports andcontains an O-ring sealing gasket 61.; Knurled adjustment knob 65, integrally connected with and externally mounted to the pressure range adjustment end piece, permits the'threaded longitudinal movement ofr end piece'SS, and thus permits externally selected variation in the forceV of compressed coiled spring 54; Surrounding the timing-piston are annular peripheral 1d l i sealing gaskets 68, 69, and 70, which gaskets are in firm fluid-tight contact with the Iinternal surface of the timing body cavity, thereby dividing this cavity into four separate fluid-tight compartments.

The first timing compartment 71 comprises that space located forward of the forward face of the timing piston and peripheral ring projection 62, and thus has for an effective 'cross section area the total area defined by the diameter of timing body cavity 53. The second and third timing compartments 72 and 73 are doughnut-shaped compartments comprising the spaces between the sides of the timing piston and the ring projections on this piston, and the internal surface of the timing body cavity. The fourth timing compartment 74 comprises that space to the rear of the rear'face of the timing piston and ring projection 64, that is, thespace occupied in part by coiled spring 54. Its effective cross section area, like that of first timing compartment 71, is the area defined by the diameter of timing body cavity 53.

For purposes of the description thus far, it is Within the scope of the present invention and the knowledge of a person skilled in the art that the uid sealing means specifically represented by the several O-ring sealing gaskets may be varied in shape, size and material. Thus,` for example, the O-ring sealing gaskets may be composed of leather, rubber, synthetic rubber, polyolefinic plastics like polyethylene, soft metals, and the like or any combination provided only that fluid-tight reciprocating motion is permitted of the timing and actuator pistons. Also, rather than being O-rings, the fluid sealing means may be of the split ring kind or overlapping split rings of suitable shape and size to provide a fluid seal. In some operations Iit is possible to use in conjunction with sealing fluids metal-to-rnetal fluid sealing means.

Additionally, accumulator vessel 60 has been described and illustrated as being of fixed, predetermined volume, but of course an accumulator of variable volume may be employed if desired. For example, a variable volume accumulator can be provided by employing a vessel containing an externally controlled, fluid-tight piston, thereby permitting a rapid change in effective accumulatorV volume by adjustment .of the longitudinal position of the piston within the vessel. Further in the apparatus embodiment of this invention so far described and illustrated the accumulator vessel is mounted partly on the timing body and partly on the actuator body, but it is recognized that the accumulator vessel can be mounted entirely on either the timing body or the actuator body or even separately and apart from both of these bodies. In certain operations as later described the accumulator vessel can be el-iminated altogether, although its use in most embodiments of the present invetnion is preferred. Still further the timing and actuator bodies 4have been shown in a straight line relationship, but these bodies may also be conveniently separated in some operations or placed in side-by-side or other relationship depending upon the needs of the particular overall combination in which the timing apparatus is to be used.

In communication at all times with third timing compartment 73 through a pressure port 75 and suitable conduit means 75A is a source `of fluid lat a relatively high pressure, or, specifically and preferably, a gaseous pressure source such as air compressor 76. Third timing compartment 73 and second timing compartment 72 are alternately in fluid communication with fourth actuator compartment 48 through conduit 77 known as a decreasing pressure conduit. In communication with first timing compartment 71 is a timing piston port 78 connecting the first timing compartment to the interior of accumulator vessel 6l). Further, tourt-h timing compartment 74 and third timing compartment 73 are alternately in communication with first actuator compartment through conduit 79 known as an increasing pressure conduit. In communication at all times between fourth timing compartment 74 and a region of lower pressure than the pressure maintained at pressure port 75, a region such as, for example, the atmosphere, is a rear timing body vent S0. A forward timing body vent 81 is located forward of the rear end lof decreasing pressure conduit 77, which vent provides communication at all times between second timing compartment 72 and a region of relatively low pressure such as, for example, the atmosphere, and which vent is so located that in the course of reciprocating longitudinal motion of the timing piston it provides alternately first for communication between only second timing compartment 72 and lthe atmosphere as shown in FIGURE 1, and then for communication of decreasing pressure conduit 77 through the second timing compartment with the atmosphere as shown in FIGURE 2. An actuator body vent 82 provides communication at all times between second actuator compartment 46 and a region of relatively low-pressure such as, for example, the atmosphere.

The accumulator vessel is in communication with actuator body cavity 21 and, in particular, it communicates alternately with the second and third` actuator compartments 46 and 47 through an accumulator conduit 83 having an adjustable accumulator orifice 84 such as a gas or air flow control valve or other mass fluid flow control means connected to an accumulator port SS whereby the mass fiow of fluid into and out of the accumulator port is controlled and adjusted as desired. When actuator piston 22 is in its retracted position as shown in FIGURE 1, accumulator vessel 60 is in direct communication With third actuator compartment 47, but when the actuator piston is in the forward or projected position as shown in FIGURE 2, the accumulator vessel is in communication withV second actuator compartment 46 and the region of relative lower pressure through rear actuator body vent 82, while third actuator compartment 47 is out of comhigh pressure supplied to third actuator compartment 47 is maintained at a substantially constant pressure by a pressure regulating valve 36 to provide constant operating air pressure on one side of an adjustable orifice S7 like adjustable accumulator orifice 84. From orifice 87 air at constant pressure is then introduced into third actuator compartment 47 through regulated pressure port 88. The relative positioning of accumulator port and regulated pressure port 88 is predetermined to allow the movement of actuator piston 22 to rst connect these ports with each other through third actuator compartment 47 in the retracted position of thepiston as shown in FIGURE l, and then in the projected position of the actuator piston as shown in FIGURE 2 Ito separate or disconnect these ports. v

As described, the illustrated apparatus permits the slidable alternating separate longitudinal movement of both the timing and actuator pistons within their respective enclosing or surrounding bodies ior containers by the employment of a single source of relatively high pressure fluid.

Operation of the Mechanical Action Timing Apparatus' Operation of the mechanical action timing apparatus shown in FIGURES l and 2 will be described on the basis of air from an air compressor being the fluid operating medium, although it is also within the scope of this invention that any liquid or gaseous fluid medium may be utilized. Thus, for example, the fluid medium depending on factors of availability and economy may be a hydraulic fluid like a liquid petroleum oil, an organic liquid comany combination and mixture thereof, water or some other f liquid medium. Further, the operating medium may be a gas or vapor such as liquiable .petroleum gases like methane, ethane, pentane and mixtures thereof as found in natural gases; hydrogen, helium, oxygen, rare gases, steam, or, preferably, air.

In the operation of the vapparatus shown in FIGURES l and 2, a source of fluid at a relatively high pressure is required with vents 3G, SI, and S2 discharging to t a region of relatively lower pressure which may be any pressure lower than the relatively high pressure, or even. a vacuum, or preferably the atmosphere. The following operations will be described in particular with reference to air at a relatively high pressure of between and 300 p.s.i.g., such as 75V to 100 p.s.i.g., with the relatively low pressure being that of the atmosphere.v The operation asv described will be directed toward a cycle time. period of about seconds, with internal time cycles of equal duration, ie., about 30 seconds Vfor boththe retracted and projecting actuator rod positions, although it should be I()V l against forward face 23 of actuator piston 22, and drives the timing piston 'is adjustable `by the *predeterminationy and preselectionA of the size oftheaccumulatorrvessel and the position orsize of the mass flow control means, i.e.,v

oneV or both of the adjustable orificesSd and 87.

Meanwhile, on commencing operation of the apparatus,

kair at apressure of between 80 and 100 p.s.i.g.say, 9()

p.s.i.g., yis admitted through conduit A and pressure port 75 into third timing compartment/73. AThis air flows through decreasing pressure conduit 77 to fourth actuator compartment 48. In this compartmentit exerts force f this piston to its most rearward or retracted position as stant pressure, since the only pressure required is that recognized that the total and internal cycle time periods are'matters of selection, and can range from 1 second to 24 hours, or be higher orlower.

Although the movements ofthe timing and actuator pistons will be described .on a step-bystep basis in detail, it should be borne in mind that in actual` operation the movement of the actuator piston will be quite rapid when the movement of the timing piston has uncovered certain ports and conduit ends. Thus the movement time of the actuator piston to go from or to either its retracted or projected position in comparison to its dwelling orresident time in thesepositions will be extremely small'and essentially insignicant. A Y 'c Referring now in particular to AlFlGURl-E 1, on startup of the apparatusair at a constantregulated pressure of, say, 8O p.s.i.g. is introduced from air compressor '76 through conduit means 88A extending'` therefrom, pressure regulating valve 86, pressure orice `87, ,and regu-k lated pressure port S8 into third actuator compartment 47. The position of the third actuator compartment. withy actuator piston 22 in its rearward or retracted position is such that there is direct communication between this compartment and accumulator portSSythu's, air at the regu# lated. constant pressure of p.s.i.g. passes through accumulator port S5, accumulator port adjustable ori'ce 84, and accumulator conduit 83, and bleeds into accumulator vessel 63. Y

The accumulator vessel is employed for time delay purposes; that is, the accumulator vesselv volume and the sizes of accumulator port adjustable orifice S4 and regulated pressure port adjustable orifice S7 control the rate at which air pressure builds up within accumulator vessel 60. From the accumulator vessel, air bleeds through timing piston port '78 into the first timing compartment.

sufficient to give motion to the actuator piston and rod. ModerateV variations in this pressure, suchas 5-20 p.s.i. from p.s.i.g. air compression, do not affect the timing function of the apparatus.

As timingn piston 55) is driven to the rear by iiuid force in first timing compartment 71 overcoming the compressive force of spring 54, O-ring gasket 69 separating the second and third timing compartments 72 and 73 passes the rear or left hand end of decreasing pressure conduit 77, thereby connecting fourth actuator compartment 48 to forward timing body ,vent S1 through second timing n compartment 72, and permitting the relatively high pressure air in the'fourth actuator compartment to bleed out vthrough this ventas shown in FIGURE 2. As timing Vpiston' 59 continues to move to theV rear'further comc connectingthe liirst actuator and third timing compartair pressure acting against the forward faces of ring projection 62 and timing piston Sti forces the ltiming piston to the rear overcoming the force of spring 54. The

moment when the timing piston begins to move to the Y rear depends, of course, upon factors such as the area of forward face 51 of the piston, therapidity and extent of the build-up of air pressureahead of the piston, and the compressive force .of the spring to be overcome.

the air pressure to overcome this force, and vice versa. The buildup of air pressure against the forward face of` The area of the timing piston face is lixedly predetermined,

vments 45and 73, and permitting the relatively high pressure air in the third timing compartment to liowV rapidly into the rst actuator compartment. This air acts under pressure againstitherrear faces of Vactuator piston 22V and ring projection 35, and moves the actuator piston from its retracted position shown in FIGURE 1 into its forward or projected position shown in FIGURE 2. This action thruststheexternal portion of the actuator piston v rod forwardto accomplishrthe desired mechanical action.V

The length of permissible forward movement of the actuator piston rod is controlled, within limits, by the position of stroke adjustment end piece 26. Thus, for

example, stroke adjustment end piece 25 may be either screwed in or screwed out with respect to the actuator body to shorten or Vlengthen the motion of actuator piston 22 and the external portion of actuator piston rod 25 which moves with the piston. As the actuator piston is moved forward, the piston rodv connected to it is advanced also,

vthereby providing rexternal mechanical motion for the performance of the desired timed mechanical function such'as opening or closing a valve, switch, or, the like.

When -the Vactuator piston assumes its forward position, 'O-ring 43 separating the second and third actuator, compartments 46 and 47 passes accumulator port 35, but stops shortvof regulated pressure pont 88, thus placing these two ports out of communication with each other whilesimultaneously connecting first timing compartment 71 and accumulator vessel 60, now both at a relatively high pressure, to the atmosphere through accumulator conduit 83, accumulator port adjustable orifice S4, ac'Y cumulator port 85, second actuator compartment 46, and actuator body vent S2.y This action permits air under pressure in first timing compartment 71 and accumulator .Vessel `6) to bleed out of actuator body vent 82. As this bleeding causes a decrease inair pressure in the fir-st timing compartment, the force of spring 54 returnstiming piston 50 to its 'original startingy position shown in FIG- Una 1.

In the course of forward movement of the timing piston,

IO-ring gasket 7 ti passes the rear end of increasing pressure conduit 79, thereby connecting the iirst actuator compartment 45, now at relatively high pressure, to the atmosphere through increasing pressure conduit 79, fourth timing compartment 74, and rear timing body vent Si). Thus as timing piston i) moves forward the high pressure air in the first actuator compartment is allowed to bleed out of vent 8b. Of course, the rear timing b-ody vent also allows air in the fourth timing compartment 74 to be forced out to the atmosphere as timing piston Sil moves to the rear, thereby preventing the compressive force of the air from being added to the preselected spring compressive force in opposing piston movement.

Further as 4the timing piston moves forward towards its position shown in FIGURE l, O-ring 69 passes the rear end of decreasing pressure conduit 77, and connects the source of relatively high pressure operating fluid at air compressor 76 to the low pressure region of fourth actuatorl compartment 43 through conduit 75A, pressure port 75, third timing compartment 73, and the decreasing pressure conduit, thereby causing the actuator piston to be forced back to its rearward or retracted position by the now relatively high pressure air in the fourth actuator compartment while the air under pressure in -first actuator compartment 45 is being vented out through rear timing body vent titl. This action of the timing piston also places 0ring sealing gasket 69 between the rear end of decreasing pressure conduit 77 and forward timing body vent 31, thereby disconnecting this conduit and vent. Of course the rearward movement of the actuator piston retracts the actuator piston rod, thereby returning this rod to its original position shown in FIGURE 1, and effecting the desired timed mechanical result such as the opening and closing or switching of a valve as in FIG- URE 3. This action then returns both the timing and actuator pistons to their starting positions, and thus completes one cyclic operation which then continues to repeat itself in .the manner previously described.

In the selection of diameter of the actuator body cavity and actuator piston, recognition should be given to the threshold level of force needed to effectuate the mechanical action desired. The diameter of actuator piston 22 taken together with its ring projections should normally be preselected in conjunction with the pressure expected to be available at pressure port 75 to give :the required amount of force to the actuator piston and its rod` 25 as they move alternatingly between their retracted and projected or projecting positions. The diameter of timing body cavity 53 and piston 5t) is not a matter of concern since any diameter sutiicient to provide operation in the manner described can be employed, but whenv the mechanical action desired requires a certain minimum force the diameter of the actuator body cavity and piston may be of importance.

When slow or remote mechanical action is desired or when the mechanical force required is high, for example 1,600 pounds or greater, timing body 4() and actuator body 2i) containing an actuator piston without an actuator rod, both bodies being of convenient size, can be positioned at a convenient remote locality. In this situation the high force mechanical action can be obtained by connecting increasing pressure conduit 79 and the decreasing pressure conduit 77 to either side of a Huid-tight container having a movable slave piston therein at a different locality. The diameter of the slave piston will be predetermined and suiiiciently great to obtain the mechanical force desired. This piston will have connected thereto a rigid piston rod extending externally of the iiuid container'and connected "with a mechanical acting valve or other device desired tobe' operated. As the remote actuator piston moves from a retracted to a projected position, the slave piston actuated by the change in fluid pressure in the decreasing and increasing pressure/conduits will likewise move with the desired force. In this manner, the size of the actuator piston can be relatively small, with the slave piston diameter of larger preselected size. e

Referring next to FIGURE 3, there is shown a schematic and partially cross-sectional view of a mechanical action timing apparatus 1t)y in operating combination with an air compressor 76, a fractionating apparatus 350 as described in the Skarstrom patent, and a four-way veported fluid ow directing valve means 200. In the combination illustrated the sole source of motive power for the timing apparatus is the relatively high pressure and at least somewhat moist stream of air from compressor 76, which moist air is also the fluid medium to befrractionated, in this case to have a substantial part of its water vapor content removed. The relatively high pressure moist air from the air compressor, is supplied to pressure port 75 and regulated pressure port Sti of mechanical timing apparatus 10 in the manner first shown in FIGURE 1, and Ito inlet port 223 of ilow directing valve means 200.

Valve means 200 shown in cross sectional view is a spool-type ow directing valve which comprises an external valve body 210 having mounted internally therein a double spool-type pistonl or plunger 215 carrying a series of circumferentially disposed fluid sealing means or O-ring sealing gaskets mounted in annular grooves. These gaskets provide fluid seals between the, internal surface of valve body 210 and the spool-type piston,

thereby defining within the valve body two annular this lfor avoidance of certain operating difliculties will .i

become apparent in the course of description of FIGURES 4 and 5. integrally connected with piston 215 and projecting axially and externally from valve body 210 is an operating arm 22@ in line with actuator piston rod 25 of the timing apparatus, and mechanically connected thereto by an outer sleeve coupling 219. i

, Spool-type piston 215 is adaptedkfor slidable, reciproeating, duid-tight longitudinal movement within valve body 21), and is responsive to 4the action of the mechanicaliy coupled actuator piston rod as this rod alternately and cyclically assumes retracted and projected positions as previously described. The motion of piston 215 directs the working fluid or moist air incoming to valve means 20h from compressor 76 to a series of ports in communication with compartments 231 and 232, and thereby effects fiow directing action by the particular dwell positions of the spool-type piston. Providing uid communication to and from the interior valve body 210 are a series of ports as follows: first vessel port 2271, second vessel port 222, inlet port 223, first exhaust port 224, vand second exhaust port 225.

Fractionating apparatus 300 as shown comprises a first adsorption vessel 301 and a second adsorption vessel 362, each of which contains a bed of solid subdivided adsorbent material having a selected affinity for one 'or more key components of the relatively high prsure stream of gaseous mixture material supplied to valve inlet port 223 as a feed stream for fractionation. In this case the feed stream is moist air, with the adsorbent material (-such as 4 x l2 mesh 4X molecular sieves) having a selected affinity for water vapor. Vessels 301 and 302 have first and second gross primary eflluent conduits 132 and 133 extending upwardly from them respectively. These con' v lduits are connected to a common discharge manifold conduit 134 which is connected in turn to a common net primary efiiuent .discharge conduit 135 containing van adjustable control valve 136. Y Connecting the first and sec" ond gross primary efuent conduits is a divided conduit 136A joined part Way along its length with a reflux conduit 137 in which is disposed a pressure reducing control valve 138. The members 139, 149, 141, and 142 designate check valves inthe just-described conduit system adapted to permit uid flows only in the directions shown.

The lower portions of vessels Stlland 302 and the adsorbent beds within them are in direct fluid communication through suitable conduit means with rst and second vessel ports 221and 222 respectively of valve bodyY 2li), with first and second exhaust ports 224V and225 of the valve body being in communication with a region of relative low pressure, in this case the atmosphere. Fractionating apparatus 300 is essentially the apparatus illustrated in FIGURE l of the Sliarstrom patent of which apparatus according to the method recited in this patent each Vessel is alternately and cyclically placed on a relatively high pressure or adsorption cycle while the other vessel is on a relatively low pressure or desorption cycle, thereby fractionating the gaseous mixture feed stream into a net primary eiiiuent stream and Va gross secondary eiiiuent stream, respectively containing the key component material in a less and greater concentration than that in which it is present in the feedA stream.

In the operation of the described apparatus combination of FIGURE 3, high pressure moist air from air' com-k pressor 76 is supplied to mechanical action timing apparatus whereby actuator piston rod 25 is alternatelyv tion cycle. At the Sametime, as shown in FIGURE 3, i

second adsorption vessel 362 previously on a high pressure or adsorption cycle is put in communication Vwith the atmosphere through second exhaust port 22S, and is therebyplaced on a low pressure or desorption cycle. p

As illustrated, moist Yair introduced into. inlet port 223 is permitted by the particularly shown position of valvev vpiston 215 to pass about this piston through compartment 231, thenY through first vessel port 22, and finally aiedaee l t2 t timed introduction into anddischarge from fractionating apparatus 36) of the same fluid medium, i.e., air, which is employed to operate mechanical action timing apparatus le. Thev unique advantages and econo-my of op- Cileration of such a combination Will 'be readily apparent toa person skilled in theV art.' As described and illustrated, a two-vessel fractionating apparatus is employed, and indeed is preferred. It is to be recognized, however, that this general combinati-on will also be operative with a fractionating apparatus having either only one or more than two adsorption vessels. Additionally, the particular flow directing valve means described, and taking the place Y ofthe two 3-way rotating plug type valves shown in the Skarstrom patent, has been employed in order to show the use of a timing apparatus having an actuator piston rod connected directly `to the moving valve port. However, timing apparatus 10 could obviously be connected indirectly, as by a yoke, to the actuating levers or linkages of the two 3-way valves shown in the Skarstrom patent tolprovide proper operation of bothof these valves. Further, two or more mechanical action timing apparatus'es can beemployed as desired, and operated with the ,same or a diiferent fluid medium from the material to be fractionated. Further still, although the uid fractionated according to the description of FIGURE 3 was moist air, the unique apparatus combination illustrated in this iigure may, of course,'be employed for the fractionation of a variety of-gaseous mixtures. Y

T z'mingA Adjustments As described, the total external cycle 'time of the apparatus of FIGURES l and 2 is that period of time that it takes from the start of motion for the actuator piston and piston rody toV move from their retracted position in main there until the start of another forward movement.

be introduced into the lower portion of 'rst adsorption Y vessel 301. Simultaneously, the Yfeed stream rof moistV air is blocked by valve piston 215'and at least one of its 0- ring sealing gaskets from entering the lower-portion ofl second adsorption vessel 302 while this vessel is in communication with the atmosphere through second vessel port 222compartment 232, and second exhaust port 225. When actuator piston Yrod- V Ymoves to its retracted position, the position of spool-type piston 215 is altered to the left, and the air flow switched to place adsorption vessels 301 `and 302 on low and high pressure or desorption and adsorption cycles respectively. In this manner, the moist air at relatively high pressure is introduced alternately and cyclically into each vessel of the two-vessel Y fractionating apparatus, and a continuous net primary effluent stream of dry airis discharged fromjoonduit 135, While the gross secondary efiiuent stream comprisingmoist air at a relatively low pressure and with a greater YwaterV vapor content than the moist airV of the feed'rstream is alternately and cyclically discharged to the atmospherel throughthe first andsecondexhaust ports 224 and 225 of ow directing valve means 2010. The term netY primary effluent refers to the kgross primary eiiiuent discharged fromkthe adsorption vessel on a high pressure or adsorption cycle less the refluxv portion thereof used to backwash the bed of adsorbent material in the vessel on a low pressure or desorption cycle, while-theA term grosssecl l'ondary effluent refers to the refluxwmaterial plus the previously adsorbed key component material desorbed and discharged from the bed of adsorbent materialy inthe vessel on a low pressure or desorption cycle.

It will be seen that the apparatus, combination shown in FIGURE 3 provides altogether suitably for the cyclical,

the actuator body toy ytheir projected or forward position therein and therebeyond; Vremainin this position for a while;.retu'rn to their initial retracted position, and re- This total cycle time can'xbe divided into tw'o internal or individual'timeV periods, a retracted time period and a forward or projected time period. The retracted time period corresponds substantiallyto that period of dwell rtime during which the actuator-piston and piston rod are in their most rearward orretracted position shown in FIGURE l, while the forward timel period corresponds substantially to'that period of dwell time during which thejactuator piston andpiston rod are in their most forward or projected position shownin FIGURE 2, the times lof'actual movement of the actuator piston back and forth between forward and retracted positions being considered negligible.

The retracted and forward time periods of the actuator piston and piston rod can be described in terms of the' motion of timing piston 50.

On this basis, the retracted time period extends substantially from the time when O-ring` 69 passes the left hand end of decreasing pressure conduit-77 asl'the timing piston moves rightwardly or forwardly `to-the time when O-ring passes the left hand endA of. increasing pressure conduit 79 as the timing piston moves leftwardly or rearwardly. On the same basis, .the foward or projected time period extends substantially from the time when O-ring 70 passes the left ,hand end of increasing pressure conduit 79 as the tim- Ying piston moves leftwardly or rearwardly tothe time when O-ring`69 passes the left hand end of decreasing lpressure'conduit '77 'as the timing piston moves rightwardly or'forwardly. The total external cycle 'time as defined can be ad- `fjusted by several methods and means which have for their purpose increasing ordecreasing as desired the delay time needed for accumulatorfvessel 60Y and ir'st timing' compartment 71 to acquire lsuiiicient internalV pressure to overcome the yforcevof compression spring 54 and start the motion of timing piston 50 leftwardly, or, conversely, when the accumulator vessel and first timing compartment are fully pressurized .the delay time needed v for them to relieve their pressure through actuator body vent 82 until the uid medium force or gas force exerted against the front face or front end of the timing piston has fallen below the spring force exerted against its rear end allowing spring 54 to start to move timing piston 50 rightwardly. One method or means of accomplishing this is to employ an accumulator vessel of widely variable volume or a succession of accumulator vessels of vvarious volumes as needed, but this is not the most suitable means or method unless the change m total cycle time desired is rather great, for example, from 30 seconds lto 10 minutes. The preferred methodis to adjust the rate of mass ow of the working iiuid, preferably air, into and out of accumulator vessel 60 and first timing compartment 71 by the use of adjustable accumulator oriiice 84.

By closing the adjustable accumulator oriiice, i.e., decreasing the size o-f its orifice opening, the mass dow rate of fluid medium or working tiuid medium or working uid into the accumulator vessel and the first timing compartment from relatively high pressure source 76 as in FGURE 1 is reduced, and the delay time for accumulator vessel 60 and first timing compartment 7l to reach a sufiiciently high pressure to acutate the timing piston in rearward movement is increased, thus increasing the dwell time of the actuator piston and piston rod in their retracted position. Opening adjustable accumulator orifice 84 has 4the opposite effect. Also, by the action of closing adjustable accumulator orifice S4 the mass flow rate of the fluid medium out of accumulator vessel 60 and first timing compartment 71 through actuator body vent 82 as in FIGURE 2 is reduced, and the delay time for the accumulator vessel and the first timing compartment to reach a sulhciently low pressure to permit spring 54 to actuate the timing piston in forward movement is increased, thus increasing the dwell time of the actuator piston yand piston rod in their projected or forward position. Opening adjustable accumlator orifice 84 has the opposite effect. It will be seen, therefore, that adjustment of orifice 84 can be used to control that total cyclic time period by either increasing or decreasing both the dwell times or internal or individual cycle time periods together.

Note is to be taken that upon the charging of accumulator vessel 60 the working uid medium at relatively high pressure, such as air from compressor '76, flows in through both adjustable pressure orifice 37 and adjustable accumulator orifice S4. Upon the discharging of the accumulator vessel, however, the uid medium iiows out through adjustable accumulator orifice 84 but not through adjustable pressure orifice 87. Accordingly, adjustment of orifice 87 will have an effect upon only the charging time of the accumulator vessel, not its discharging time. Said in other words, adjustment of orifice 87 will have an effect upon only the dwell time of the actuator piston and piston rod in their retracted position, not their dwell time in their forward or projected position. Closing adjustable pressure orifice 87 increases the retracted dwell time of the actuator piston and piston rod while opening it decreases this dwell time.

Independent setting of the dwell times of the actuator piston and piston rod in their retracted and forward positions can be achieved by adjusting both orifices 34 and 87. With an initial arbitrary or intermediate adjustment of pressure orifice 87, accumulator orifice 84 is adjusted as necessary to give the desired forward dwell time of the accumulator piston and piston rod. Of course this adjustment will also provide some particular retracted dwell time of the actuator piston and piston rod, but not necessarily the desired one, and indeed probably not the desired one. The desired retracted dwell time is obtained by adjusting pressure orifice 37 as necessary. Fluid pressure on the upstream side of the adjustable pressure orifice is' maintained substantially constant by pressure regulating Valve S5. Thus a given combination of adjustments of orifices 84 and 87 will provide repeatable values of the dwell times of actuator piston 22 and its piston rod 25 in their retracted and forward positions assuming, of course, that the region of relatively low pressure with which actuator body vent 82 communicates is also a region of relatively constant pressure.

It is possible, as a matter of fact, that a mechanicalv action timing apparatus could be built and operated without either or both of the adjustable orifices 84 and 87, or, equivalently, with one orifice adjustable and the other fixed, or with both fixed. From the foregoing description it will be clear what the impairment of utility of the timing apparatus would be in respect of loss of adjustability of either or both total and individual cycle times for any particular one of these design modiications.` In the design of any given apparatus embodiment of timing apparatus 10 as shown, that is, the apparatus having both adjustable orifices 84 land S7, proper consideration must, of course, be given to conditions of fiow of the fluid operating medium through the orifices and ports of the apparatus, especially to any conditions of critical flow which might affect the stability or desired range of adjustment of the total and individual cycle times.

In an apparatus in which the diameter of the timing piston is relatively large and for which the total timing cycle period is required to be relatively short, e.g., 1 to 30 seconds, it is possible for the timing apparatus to function without an external accumulator Vessel. 'In this case the necessary time delays of pressurizing and discharging can be obtained by utilizing the volume of iirst timing compartment 71 only, and so accumulator conduit 83 is brought directly to timing piston port 78 while accumulator vessel 60 is removed entirely. In apparatuses in which smaller diameter timing pistons are employed and for which longer total timing cycle periods are required, however, it is preferred that external accumulator vessels be utilized. One of the difficulties associated with use of the first timing compartment as an accumulator arises out of the need to reduce the timing piston port diameter. Such reduction increases the danger of having this port become plugged by dirt, heavy oil, rust particles, or other solid or liquid contaminants inthe tluid operating medium. For example, where' the timing piston port of lan-apparatus having an external accumulator vessel is about 0.010 to 0.020 inch in diameter for a delay period of 30 seconds, the same delay period for this apparatus used without an external accumulator vessel would require that the apparatus have.

a timing piston port of only about 0.001 to 0.005 inch diameter. A port of this small size would be quite susceptible to plugging.

Another suitable method of adjusting at least one of the internal or individual cycle time periods as well as the total timing cycle of the apparatus is by controlling the longitudinal position of pressure range adjustment end piece 5S. Forward adjustment of this end piece by means of its external knob 62 increases the force exerted by spring Srl against rear face 52 of timing piston 50, and thereby increases the fluid operating medium force and consequently the pressure accumulation time required to overcome the spring force. Thus by increasing the initial spring compression the dwell or residence time of the actuator piston and piston rod in their retracted position may be increased. Conversely, where there is an initial preset force of spring 54 against the timing piston, rearward adjustment of pressure range adjustment end piece 5S decreases the dwell time of the actuator piston and piston rod in their retracted position.

.All of the adjusting methods described can, of course, be used either separately or in combination to obtain the desired effect on both the total and individual cycle time periods. Another method would involve the structural alterationof substituting a pneumatic resilient or biasing aieonse i means for coil spring'54, and call `for variation `of the initial condition of pressurization of this means. Said in other words and for example, rear timing body vent 86 could be plugged to trap a body of airv in fourth timing compartment 74 to serve as a pneumatic spring,

and the initial compression of this spring varied according to the longitudinal position or" end piece 55.Y Additionally, the same effect could be achieved without adV justment of end piece 55 by connecting vent 30 to av source of air pressure capable of being regulated. yThe peak value of this regulatedY pressure would, of course, have to be lless than the pressure available from air compressor 76 in order that leftward or' rearward motion ci timing piston Si) still be possible.

Infernal Fluid Flow Directing Timing Apparatus of' actuator body 112, is provided with additional annular' peripheral ring projections 113, 114,l and 11S.' CradledV and supported in annular recesses in these three ring projections respectively are 0ring sealing gaskets 117, 118,-

and 119 which are in iirm, fluid-tight'contact with the internal surface of the actuator body cavity. manner the actuator body cavity is divided up into three additional fluid-tight, doughnut-shaped compartments. Two of these additional compartments areiirst and second exhaust compartments 122 and 124 which are in separate communication at all times with a region of relatively low pressure, for example, the atmosphere, through first and second exhaust vents 125 and 126 respectively. The third additional .compartment is fluid feed stream directing compartment 123 which is in communication at all times with a Ifeed port 127.r In the embodiment shown, this feed port in turn is in communication by means of conduit 127A with a source'of relatively high pressure tiuid suchV as an air compressor 76 which also supplies the fluid medium or air to operate the timing apparatus. In this embodiment air constitutes both the fluid operating medium of the timing apparatus and the iiuid to be directed by the internal fluid iioW directing means. Y

First and second exhaust compartments 1'22 and 124 are alternately in communication through first and second inlet-outlet flow directing ports 128 and 129 with first and second adsorption vessels 13@ and 131 respectively. It is these vessels into which it is desired to introduce alternately a relatively high pressure stream of moist air in a preselected timed manner according to the teachings of the Skarstrom patent. Thus these vessels contain beds of an adsorbent material having a selective affinity for one or more components of the gaseous mixturerfeed stream, such asin this case the water vapor content of the moist air discharged from compressor 76.

As described herein, the internal iiuid dow directing timing appartaus of FIGURES 4 and 5 is in combination and fluid flow communication with aheatless fractionating apparatus. It is to be recognized, of course, that flow directing means of the general kind described can be employed to alternately direct any types of fluids,

In this o f il@ doesA not Ihave 'connected to it an' actuator piston rod projecting externally 'from this timing apparatus. A stroke adjusting end piece 151, with a knurled adjustment knob 152, isV provided in order to permit minor j adjustments to be made in the extreme forward position of the actuator piston, for example, to obtain the proper positioning of the actuator piston AO-rings along the actuator body cavity internal surface. vAdditionally, of course, the iiow directing timing apparatus can be provided with an actuator piston rod, if desired, and thus be capable ot furnishingboth external mechanical action and internal fluid flow direction.

The operation o thetiming apparatus portion of the whole apparatusV of FIGURES 4 and 5 is as previously described in connection with FIGURES l and 2. FIG- URE 4 shows the actuator piston in its retracted position permitting relatively high pressure moist air from air compressor '76 to enter feed port 127; flow through feed stream directing compartment 123 and first inlet-outlet iiow directing port 12S, and be introduced into the lower portion of first adsorption vessel 130, thereby placing this vessel on a high pressure or adsorption cycle. At this i time second adsorption vessel 131 previouslyv on a high 'pressure or adsorption cycle is'or is placed ona low pressure or desorption cycle by being or .being put in communication ,with the atmosphere through second inletoutletV flow directing port 129, second exhaust compartment 124, and second exhaust vent 126, thereby permitting the discharge from vessel 131 of a gross secondary eiiiuent stream. The net primary effluent stream, i.e., the desired dry product air, fiows out through the high pressure discharge conduit of the Skarstrom apparatus as shown.

When timing piston 50 is forced rearwardly by increasing air pressure within accumulator vessel and first timing compartment 71, actuator piston is moved` forwardly to its position shown in FIGURE 5. In this position of the actuator piston the iiow of relatively high pressure moistV air into firstV adsorption vessel 130 is stopped by the positioning of VO-ring 11S between rst inlet-outlet flow directing port 128 and feed port 127, and correspondingly the vfirst adsorption vessel is shifted onto a low pressure or desorption cycle by being put in communication lwith the atmosphere through first inletoutlet flow directing port 128, iirst exhaust compartment 122, and first exhaust vent 125. At the same time flow of relativelyhig'n pressure moist air is commenced into the lower portion of second adsorption vessel 131 placing ,this vessel, previous-ly on a low pressure or desorption cycle, onto a high pressure or adsorption cycle. In this mannerVthe-air is alternately and cyclically introduced into and discharged from the first and second adsorption Y vessels in a preselected timed manner to cause the fracgaseous or liquid, into any sort or number of separate vessels, pipelines, containers, tanks, and the like either tionation ofVv the `feed stream of relatively high pressure moist air into streams of dry air and air of increased moisture Vcontent according to the heatless fractionation method. 'The adsorbent material of the beds within vessels 13u and 131 may be any subdivided solid material haivng a selective ainity for water Vapor, for example, a materialsuch as 8 x 12 mesh -4 molecular sieves, charcoal, silica gel, etc.

Utilization 0f Apparatus The mechanical action timing apparatus of this invention shown in FIGURES l and 2 had particular utility as j shown in FIGURE 3 in combination with those adsorptivetype fractionat-ing apparatuses rated Vfor relatively large gas ows such as 50 standard cubic feet per-,minute (50 s.c.t`.n1.) or higher. The internal iiuid ilow directing timing apparatus shown in FIGURES 4` and 5 is of general utility in combination with fractionating apparatuses rated for somewhat smaller gas ows, especially relatively low gas iiows in the range from about 1/2 s.c.f.m. to about 10 s.c.f.m. For high-flow Ifractionating apparatuses, the mechanical faction timing yapparatus Will operate the ow switching valves or flow directing means by shifting the l 7 valves through the movement of its actuator piston rod. Mechanical shifting action is preferred for theiiow switching valve means of high-flow fractionating apparatuses because the inlet-outlet flow directing ports 123 and 129 of a timing apparatus 100 according to FlGURES 4 and S used with such a fractionating apparatus would of necessity be fairly large, for example over Y1/2 inch or over 1 inch in diameter to avoid excessive pressure drop of fluids flowing through them. However, the use of such large diameter ports will not be entirely acceptable in all cases on account of the tendency of O-ring sealing gaskets 117 and 118 to be extruded into the ports. Therefore, where linlet-outlet ports of the larger size would be required external operation of the flow directing valve means Iis preferred, while where these ports can properly be less than 1A: inch or less than 1A; inch in diameter with low-flow fractionating apparatuses the timing apparatus of FIG- URES 4 and 5 with internal fluid flow directing means is preferred. Although both timing apparatuses described are particularly suitable to provide total cycle times of 30 seconds to 60 minutes, eg., l minute to 20 minutes, longer or shorter total cycle times are possible as well as equal or unequal periods of forward and retracted actuator piston dwell.

Conclusion rl`he present invention has been described and illustrated in and with certain preferred but nonlimiting specific apparatus embodiments and modes of operation, and at least some modifications of it in detail within the capabalities of a person skilled in the artupon his consideration of this disclosure .are contemplated. It is intended to secure protection by Letters Patent of all these modifications within the spirit and scope of the appended claims tothe broadest extent that the prior yart permits.

I claim as my invention:

1. A mechanical action timing apparatus comprising in combination l) '-an accumulator vessel;

(2) a timing body having a forward end and a rear end and having disposed therein for reciprocating motion a timing piston having a rear face and a forward face which piston divides the timing body into at least four fluid tight compartments as follows:

' (a) a first timing compartment having the forward face of the piston `as one side thereof land the forward end of the timing body as the opposite side thereof and being in fluid communication through a timing port with the accumulator vessel,

(b) a second timing compartment in fluid communication through -a forward discharge vent with a region of relatively low pressure,

(c) a third timing compartment capable of being placed in fiuid communication with a relatively high pressure source through a pressure port, and

(d) a fourth timing compartment having the rear end of the timing piston as one side thereof, and the rear end of the timing body as the opposite side thereof and having ldisposed therein a resilient means to return the timing piston to a forward position;

(3) an actuator body having a forward end and a rear end land having disposed therein for reciprocating motion an actuator piston having a rear face and a forward face and having an actuator piston rod integrally mounted with said piston for movement therewith, said rod projecting in a fluid tight manner externally of the timing body, which piston divides the actuator body into at least four uid tight compartments as follows:

(a) a rst actuator compartment having the rear face of the actuator piston as one side thereof and the rear end of the actuator body as the pposite side thereof,

(b) a second actuator compartment in fluid communication through an actuator discharge vent with a region of relatively low pressure,

(c) a third actuator compartment capable ofbeing placed in uid communication through alregulated pressure port with a source of relatively constant pressure, and

(d) a fourth actuator compartment having theforward face of the actuator piston as one side thereof and the forward end of the actuator body as the opposite side thereof;

(4) a decreasing pressure conduit in fluid communication at one end with the fourth actuator compartment and being so disposed that it is in -alternate duid communication at another end with the third andsecond timing compartments by the reciprocating motion of the timing piston;

(5) an increasing pressure-conduit inuid communication at one end with the first actuator compartment and being so disposed that it is in alternate fluid communication at another end with the fourth and third timing compartments by reciprocating motion of the timing piston, and

(6) an accumulator conduit in fluid communication at one end with the accumulator vessel and being so disposed to be lin -alternate fluid communication at another end with the third and second actuator compartments by the reciprocating motion of the actuator piston.

2. A timing apparatus as defined in claim 1 wherein said .accumulator conduit contains fluid flow control means.

3. A timing apparatus as defined in claim 1 which includes fluid flow control means in fluid communication with the regulated pressure port.

4. A timing apparatus as defined-in claim 1 which body includes actuator piston stroke adjustment means to control the longitudinal travel of the actuator piston rod.

5. A timing yapparatus as defined in claim 1 which includes adjustment means whereby the force exerted by the resilient means on the timing piston may be regulated.

6. A timing apparatus as defined in claim `1 wherein the tim-ing and actuator pistons are cylindrically shaped bodies having circumferential fluid sealing means.

7. A timing apparatus as defined in claim 1 wherein said resilient means is a spring means. Y

8. A timing apparatus as defined in claim l in which the timing body has a rear discharge vent through which said fourth timing compartment is in fluid communica,- tion with a region of relatively low pressure.

9. A timing apparatus as defined in claim'l in combination with a source of relatively high pressure fluid, said source being in fluid communication with (a) Vthe pressure port in said timing body, and '(b) the regulated pressure port in said actuator body.

l0. An apparatus combination according to claim 9 in which said source is in fluid communication with said regulated pressure port through pressure regulating means.

11. An apparatus combination as defined by claim 9 wherein said fluid pressure source is an air pressure source.

12. An apparatus combination as defined by claim 9 wherein said actuator piston rod is operatively connected to external fluid flow directing means.

13. A timing apparatus as defined by claim l in combination with (l) a source of a relatively high pressure gaseous feed stream containing at least one key component;

(2) a gas fractionatingmeans adapted to fractionate said feed stream into one stream containing the key component in a decreased concentration and another stream containing the key component in an increased concentration by the alternating and cyclic introduction of the feed stream into and its. discharge from a vessel containing a bed of adsorbent material; and

(3) a gas iiow directing means connected to the actua.-

tor piston rod of said timing apparatus and adapted to permit the alternating and cyclic, introduction of the gaseous lfeed stream into and its discharge from saidfvessel in response to the movement of the actua- Itor piston rod; said source being also in fluid coml,

(a) a first timing compartment having the Vforward face of the piston as one side thereof and the forward end of the timing body as the opposite side thereof and being in fluid communication through a timing port with the accumulator vessel,

(b)y a 'second timing compartment in fluid communication through a forward discharge vent with a region of relatively low pressure,

(c) a third timing compartment capable ofv being t placed in uid communication with a relativeiy high pressure source through a pressure port, and Y (d) a fourth timing compartment having the rear end of the .timing piston astone side thereof, and the rear end of the timing body as the opposite side thereof and having disposed therein a coiled spring tending to return the timing piston to a forward position and being in' iiuid communication through a rear discharge vent with a region of relatively-lowppressure; Y

(3) an actuator body having a forward end and a rear end and characterized by a cavity and having disposed `therein for slidable reciprocating mot-ion a cylindn'cally shaped actuator .piston having a rear face and a forward face andvcircumferential fluid sealing means and having further an actuator piston Y rod integrally and centrally mounted withfsaid piston for movement therewith, said lrod .projecting in a slidable fluid-tight manner externally of the timing bodyrwhich .piston divides the actuator body cavity into atleast four huid-tight compartments as follows: Y Y

(a) a rst actuator compartment having the rear face ofthe actuator piston as one side thereof and the rear end of the actuator body as the opposite side thereof, Y y Y (b) a second actuator compartment in huidcommunication through an actuator discharge vent with a region of relatively low pressure,

(c) a third actuator compartment capable of being placed in fluid communication through a regulated pressure port with a source -of relatively constant pressure, and l (d) a fourth actuator compartment having the forward face of the actuator piston as one side thereof and the forward end of the actuator v body as the opposite. side thereof;

(4) a decreasing pressure conduit in uid communication at one end with the fourth actuator compartment and being so disposed `that it is in alternate u'id communication at another Vend with theY third and second timing compartments by the reciprocating motion of the timing piston;

(5) an increasing pressure conduit in uid communication at one end with the first actuator compartment and being so disposed that it is in alternate fluid communication at another end with the fourth and third timing compartments by reciprocating motion of the timing piston; and Y (6) an accumulator conduit in fluid communication at one end with the accumulator vessel and being so disposed to be in alternate fluid communication at another end with the third and seco-nd actuator compartments by the reciprocating motion of the actuator piston and containing adjustablefluid flow control means. y

v15V.` A timing apparatus as'defned in claim 14 which includes actuator piston stroke adjustment means to concommunication with the regulated pressure port.

16. A timing apparatus as defined in claim l4rwhich includes actuator piston stroke auijustment means to control the longitudinal travel of the actuator piston rod.

17. A timing Vapparatus as defined in'clairn 14 which includes adjustment means whereby the force exerted by the coiled spring on the timingpiston may be regulated.

. @18. A timing apparatusY as defined in claim 14 in combination with a source of relatively high pressure air, said source being in air communication with (a) the pressure port in said timing body,l and (b),the`regulated pressure port in said actuator body.

19. An apparatus combination according to claim 18 in which said source is in air communication with said regulatedv pressure port through pressure regulating means. I

20. 'An apparatus combination as defined by claim 18 wherein said actuator piston rod is operatively connected to external gas -ow directing means. 21. A iiow directing timing apparatus comprising in combination Y (1) an accumulator vessel; 1

(2) a timing body having-aV forward end and a rear end, and having disposed therein for reciprocating motion a timing piston having a rearface rand a forward face which piston divides the timing body into at least four fluid-tight compartments as follows:

(a) Va first timing Vcompartment having thefforward face of the piston as one side thereof and the forward end of the timing body `as, theopposite side thereof and being in iiuid communicationv through a timing port with the accumulator vessel,

(b) a second timing compartment in uid communication through a .forward discharge vent with a region of relatively low pressure,

(c) a thirdtiming compartment capable of being placed in fluid communication with a relatively high pressurev source through a pressure port, and

(d) a fourth timing compartment having the rear end of the timing piston as one side thereof and the rear end of the timing body as the opposite side thereof, Vand having disposed therein a resilient means to return the timing piston to a forward position;

(3) an actuator body having a forward end and a rear end, iandhaving disposed therein for reciprocating motion an actuator piston having a rear face and a forward face, which piston divides the actuator body into at least yseven fluid-tight compartments as follows:

(a) a rst actuator compartment having the rear face of thefactuator piston as one side thereof Y'and the rear end of the actuator body las the opposite sidethereof, y

(b) a second actuator compartment in fluid communication through an actuator discharge vent withfya region of relatively low pressure,

(c) a third actuator compartment capable of being placed in fluid .communication through a 21 22 regulated pressure port with a source of reladisposed to be in 'alternate uid communication at tively constant pressure, another end with the third and second actuator com- (d) a rst exhaust compartment having a first partments by the reciprocating motion of the actuainlet-outlet port and in uid communication tor piston.

through a first exhaust vent with a region of r 22. A 110W directing timing appartus as defined in relatively 10W pressure, o claim 21 in combination with (e) a feed stream compartment in liuid corn- (1) a source of a relatively high pressure gaseous feed munication With a feed stream port and in alstream containing at least onekey component, said ternate fluid communication with iirst and secsource being in gaseous communication with ond inlet-outlet ports by the reciprocating mo- (a) the pressure port, tion of the actuator piston; 10 (b) the regulated pressure port through a pres- (f) a second exhaust compartment having a secsure regulating means', and ond inlet-outlet port and in iiuid communica- (c) the feed stream port; and tion through a second exhaust vent with a re- (2) a fractionating apparatus comprising Aa first and gion of relatively loW pressure, and la second vessel, each vessel containing a bed of l (g) a fourth actuator compartment having the 15 adsorbent material having a selected afiinity for said forward face of the actuator piston as one side key component and said irst and second vessels thereof and the forward end of the actuator being in respective gas communication with the rst body as the opposite side thereof; and second inlet-outlet ports.

(4) a decreasing pressure conduit in fluid communication at one end with the fourth actuator compart- 20 References Cited 111 the 111e 0f this Pil'leilt ment and being so disposed that it is in alternate i UNITED ASTATES PATENTS iluid communication at another end With the third and second timing compartments by the recipro- 1,887,589 Farmer Nov. 1,5, 1932 cating motion of the timing piston; 1,887,606 Thomas Nov. 15, V'1932 cation at one end with the tirst actuator eompart- 2,093,805 Baufre Sept. 21, 1937 ment and being so disposed that it is in alternate 2,380,315 Kilian July 10, 1945 and third timing compartments by reciprocating mo- 30 2,651,061 Polleys Sept. 8, 1953 tion of the timing piston; and 2,768,703 Parks Oct. 30, 1956 `one end with the accumulator vessel and being so UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No., 3, 160,486 December 8q 1964 Adolphus L BuschY .Iro

v It is hereby certified that error appears in the above numbered patent requiring correction and that the said Letters Patent should read as corrected below.

Column 2O lines l2 to lli, strike out "A timing appara tuf -Tas-defined in claim 14 which includes actuator pis-os stroke adjustment means to concommunication with the pressure port." and insert instead A timing niagara-sas defined in claim 14 which includes adjustahe fluid jle-'.1 control means in fluid communication with the pressure port.7

Signed and sealed this 13th day of Aprillr (SEAL) Attest:

ERNEST W. SWIDER EDWARD J. BRENNER Attesting Officer Commissioner of Patents

Claims (1)

1. A MERCHANICAL ACTION TIMING APPARATUS COMPRISING IN COMBINATION (1) AN ACCUMULATOR VESSEL; (2) A TIMING BODY HAVING A FORWARD END AND A REAR END AND HAVING DISPOSED THEREIN FOR RECIPROCATING MOTION A TIMING PISTON HAVING A REAR FACE AND A FORWARD FACE WHICH PISTON DIVIDES THE TIMING BODY INTO AT LEAST FOUR FLUID TIGHT COMPARTMENTS AS FOLLOWS: (A) A FIRST TIMING COMPARTMENT HAVING THE FORWARD FACE OF THE PISTON AS ONE SIDE THEREOF AND THE FORWARD END OF THE TIMING BODY AS THE OPPOSITE SIDE THEREOF AND BEING IN FLUID COMMUNICATION THROUGH A TIMING PORT WITH THE ACCUMULATOR VESSEL, (B) A SECOND TIMING COMPARTMENT IN FLUID COMMUNICATION THROUGH A FORWARD DISCHARGE VENT WITH A REGION OF RELATIVELY LOW PRESSURE. (C) A THIRD TIMING COMPARTMENT CAPABLE OF BEING PLACED IN FLUID COMMUNICATION WITH A RELATIVELY HIGH PRESSURE SOURE THROUGH A PRESSURE PORT, AND (D) A FOURTH TIMING COMPARTMENT HAVING THE REAR END OF THE TIMING PISTON AS ONE SIDE THEREOF, AND THE REAR END OF THE TIMING BODY AS THE OPPOSITE SIDE THEREOF AND HAVING DISPOSED THEREIN A RESILIENT MEANS TO RETURN THE TIMING PISTON TO A FORWARD POSITION; (3) AN ACTUATOR BODY HAVING A FORWARD END AND A REAR END AND HAVING DISPOSED THEREIN FOR RECIPROCATING MOTION AN ACTUATOR PISTON HAVING A REAR FACE AND A FORWARD FACE AND HAVING AN ACTUATOR PISTON ROD INTEGRALLY MOUNTED WITH SAID PISTON FOR MOVEMENT THEREWITH, SAID ROD PROJECTING IN A FLUID TIGHT MANNER EXTERNALLY OF THE TIMING BODY, WHICH PISTON DIVIDES THE ACTUATOR BODY INTO AT LEAST FOUR FLUID TIGHT COMPARTMENTS AS FOLLOWS:

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